|Publication number||US4629039 A|
|Application number||US 06/816,051|
|Publication date||Dec 16, 1986|
|Filing date||Jan 3, 1986|
|Priority date||Jan 17, 1985|
|Also published as||DE3600733A1|
|Publication number||06816051, 816051, US 4629039 A, US 4629039A, US-A-4629039, US4629039 A, US4629039A|
|Inventors||Yuzo Imoto, Yoshiyuki Hattori, Toshihiro Takei, Taro Tanaka|
|Original Assignee||Nippondenso Co., Ltd, Nippon Soken, Inc.|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (10), Non-Patent Citations (2), Referenced by (59), Classifications (30), Legal Events (5)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This invention relates generally to a braking control apparatus for a vehicle, such as an automobile, in which the braking action is based on a command resulting from the operation of a brake pedal, and more particularly, to a braking control apparatus which avoids the problem of slippage occurring due to the wheels locking, to thereby provide stable braking control.
The braking device provided for each wheel is operated by the pressure of the brake fluid. Brake fluid under pressure is supplied to each wheel cylinder from the master cylinder by the operation of the brake pedal. This brake fluid drives the brake piston provided in the wheel cylinder for applying a braking force against the rotary brake disc which is provided coaxial with the wheel of the automobile.
A piston, which is operated by the brake pedal to generate brake fluid pressure, is provided inside the master cylinder which is positioned near the driver's seat. Between the master cylinder and each wheel is located a brake pipe for the transmission of the brake fluid. An increase in the pressure results in the brake pipe expanding and changes in the compression of the fluid in the pipe, which in turn is the source of delays in pressure transmission.
When, upon operation of the brake pedal, the wheels begin to slip in relation to the ground and then lock, it is necessary that the braking force be immediately reduced to unlock the wheels and prevent slippage. What is desired is an antiskid control apparatus which detects the locking of the wheels and automatically controls the braking force. Various means have been considered for this kind of antiskid control apparatus.
For example, when wheel lock is detected, an electromagnetic valve, which is provided in the fluid passage between the master cylinder and the wheel cylinder, reduces the pressure of the fluid supplied to the wheel cylinder. In this case, however, any delay in transmission will result in a delay in response to the antilock operation, and any structure that improves the responsiveness is difficult to build.
Another example is a device which uses traction control such that the rotary force of the wheels is delivered efficiently to the ground. When slippage resulting from wheel spin is detected, the electromagnetic valve is operated to control the supply of fluid pressure to the wheel cylinder where slippage has occurred. In this case, as well, response cannot be controlled because of the transmission delay in the braking system.
The object of this invention is to provide an automobile braking control apparatus, which can perform antiskid control and traction control, etc. so that the braking force of the wheels can be minutely controlled.
Another object of the invention is to provide an automobile braking control apparatus which can control the fluid pressure generated in braking device of each wheel and in which the pipes for transmitting brake fluid can be eliminated.
Another object of the invention is to provide an automobile braking control apparatus in which the braking force generated by the braking mechanism at each wheel can be independently and electronically controlled to effectively control the stable running of the automobile.
Another object of the invention is to provide an automobile braking control apparatus in which the response and reliability is improved.
In the automobile braking control apparatus of this invention a wheel cylinder is provided for each wheel of an automobile and a piezoelectric piston device in which the contraction and expansion of the piezoelectric elements is controlled by the voltage of a signal is provided for varying the volume of the wheel cylinder. The piezoelectric piston device is provided with a displacement amplification mechanism which amplifies the contraction and expansion of the piezoelectric elements in varying the volume of the wheel cylinder.
With this kind of apparatus the amount of expansion and contraction of the piezoelectric elements in response to the control voltage that is supplied is very small but large changes in wheel cylinder volume can be obtained with the displacement amplification mechanism so that the pressure acting on the brake piston in the wheel cylinder can be effectively controlled to provide effective electronic control of the braking. As control of the brake piston fluid pressure is electronic, the control is extremely responsive for very effective antiskid control, etc.
FIG. 1 shows a cross section of part of the braking control apparatus for each wheel according to the first embodiment of this invention;
FIG. 2 shows the braking control system of the above apparatus as applied to a vehicle;
FIG. 3 shows another example of a braking control system;
FIGS. 4 and 5 show still another example of a braking control;
FIG. 6 is a cross section of another example of a braking control apparatus applied to each wheel; and
FIG. 7 is a cross section of another example of a braking control apparatus.
FIG. 1 shows a braking apparatus 10 for one wheel of an automobile, the braking apparatuses for the other wheels being the same.
Braking apparatus 10 is made of metal and is formed on the inside of brake caliper 11. Wheel cylinder 12, which is formed in brake caliper 11, has a brake piston 13 to which is attached brake pad 14 and which slides in the axial direction in the cylinder. Brake pad 14 and brake piston 13 are moved together to apply pressure to brake disc 16 which is positioned between brake pad 14 and brake pad 15 which is attached to brake caliper 11. Brake disc 16 rotates together with the wheel so the vehicle is braked.
Brake piston 16 is cylindrical in shape and is partitioned on the inside by wall 17 to form first and second control cylinders 18 and 19 which are also coaxial with wheel cylinder 17. Second control cylinder 19 forms hydraulic pressure chamber 20.
Control piston 21, which is a displacement member and moves in the axial direction, is provided inside second control cylinder 19. A plurality of small pistons 221, 222, . . . are provided projecting from control piston 21 to face wall 17 and are inserted into cylinder holes formed in wall 17 so that they project into first control cylinder 18. In this embodiment there are a plurality of these small pistons but there need be only one. Springs 211 act on control piston 21 to push small pistons 221, 222 toward first control cylinder 18.
Piezoelectric piston device 24 includes a piezoelectric device 23, which comprises a plurality of laminated thin-plate piezoelectric elements 231, 232, . . . , and is provided inside first control cylinder 18. First and second plates 241 and 242 are sandwiched and held between piezoelectric elements 231, 232, . . . and first plate 241 is screwed into brake piston 13 at the first control cylinder end. Second plate 242 faces wall 17 and a hydraulic chamber 25 is formed in between. Springs 243 are located in hydraulic chamber 25 and urge second plate 242 together with piezoelectric elements 231, 232, . . . toward first plate 241.
The plurality of piezoelectric elements 231, 232, . . . that comprise piezoelectric device 23 are laminated with electrode plates (not shown) in between. These electrode plates are connected in parallel with piezoelectric elements 232, 232, . . . . When a high voltage is applied to this group of piezoelectric elements they expand and second plate 242 moves toward wall 17. More specifically what happens is that piezoelectric piston device 24 expands decreasing the volume of hydraulic chamber 25 so the volume of hydraulic chamber 25 is varied by the application of voltage to piezoelectric device 23.
Hydraulic chamber 25 is sealed and filled with brake fluid so small pistons 221, 222 are driven by the amount of the changes in the volume of hydraulic chamber 25 caused by the contraction and expansion of piezoelectric piston device 24. The surface area of the small pistons 221, 222 is less than that of the working surface of piezoelectric piston device 24 which is the surface of second plate 242 facing hydraulic chamber 25 so the displacement volume of piezoelectric piston device 24, i.e., the amount of movement of second plate 242, is amplified and transmitted to small pistons 221, 222, . . . , which drive control piston 21. The mechanism for these small pistons acts as a displacement amplifying mechanism for amplifying and transmitting the movement of piezoelectric piston device 24 to control piston 21, which is the displacement member.
Brake piston 13 is connected to brake caliper 11 at the opening of wheel cylinder 13 by coupling member 26, which is made of a flexible sheet, to thereby provide stable movement of brake piston 13 inside wheel cylinder 12.
Brake fluid is supplied from fluid passage 27, which is formed in brake caliper 11, to hydraulic chamber 20 formed in wheel cylinder 12. Fluid passage 27 is connected to the master cylinder (not shown).
Control valve 28 is provided in fluid passage 27 and the passage is opened and closed by valve plug 281. Valve plug 281 is driven by the fluid pressure in cylinder 282 in which a piezoelectric piston 283 comprising a plurality of laminated thin-plate piezoelectric elements is provided. Then when a high voltage is supplied to these piezoelectric elements and they expand, the pressure in hydraulic chamber 282 increases and valve plug 281 is driven to close passage 27.
The piezoelectric piston device 24 and control valve 28 of this kind of braking control apparatus 10 are controlled by control unit 29, which may be a microcomputer, for example. This microcomputer may also be used for controlling the engine of the automobile by receiving detection signals from surface speed and wheel speed sensors, etc. Control unit 29 controls the voltage that is supplied to the piezoelectric elements that comprise piezoelectric piston 283.
Braking control apparatus 10 described above is provided for each wheel. It is, however, possible to provide the apparatus for only the rear wheels 30, 31 and provide the front wheels 32, 33 with a conventional braking apparatus. In such a case, the rear wheels are the driving wheels and control valve 28 is provided in the fluid transmission circuit for supplying brake fluid to the particular wheel cylinders 12.
As shown in FIG. 2, when brake pedal 36 is depressed, the pressure of the brake fluid in master cylinder 37 rises and is transmitted to wheel cylinder 12 to apply a braking force on wheels 30-33 corresponding to the force applied to brake pedal 36. In the normal state, control valve 28 is open and the brake fluid is supplied directly to wheel cylinder 12 to drive brake piston 13.
When brake pedal 36 is depressed strongly while the automobile is running, the wheels will slip in relation to the ground and lock. The lock-up of the wheels constitutes an abrupt change in the rotary speed of the wheel which is detected by control unit 29. The relationship between the rotary speed of the wheel and the surface speed may also be used by control unit 29 to detect lock-up. When wheel 31 locks up, for example, control unit 29 switches the voltage supplied to piezoelectric device 23 of braking control apparatus 10 to high level. Piezoelectric piston device 24 expands and the volume inside hydraulic chamber 20 of wheel cylinder 12 is decreased. Since the pressure in hydraulic chamber 20 is determined by master cylinder 37, there is no change. Then control valve 28 closes off fluid passage 27.
By closing control valve 28 the volume of hydraulic chamber 20 of wheel cylinder 12 is kept constant and, in this state, the voltage supplied to piezoelectric device 23 of piezoelectric piston device 24 is switched to low level thereby contracting it. Brake piston 13 then pulls pad 14 from brake disc 16 and the braking force to the wheel that is locked is reduced. In this way control of the braking can be performed based on a suitable slip ratio.
Since the pressure in wheel cylinder 12 is controlled by a device inside caliper 11, it is possible to provide a very responsive antiskid control system than is also very compact. Also, since the piezoelectric device is controlled electronically by commands from control unit 29, a suitable slip rate can be set for each wheel for the most effective braking control. In this case, even if the changes to the voltage supplied to the piezoelectric elements are small and the amount of expansion and contraction is small, the amount of contraction and expansion of piezoelectric piston device 24 is large due to the amplifying action of small pistons 221, 222, . . . . Also, since the volume of hydraulic chamber 20 of wheel cylinder 12 is extremely small, control of the pressure is extremely responsive.
The above braking control apparatus 10 is not limited to this kind of antiskid control but also can perform traction control for preventing slippage that occurs due to spinning of the wheels during acceleration. During acceleration the brake is not operated and the pressure in wheel cylinder 12 is low. When it is detected that the wheels are spinning, control valve 28 is closed while piezoelectric piston device 24 of the spinning wheel is in a contracted state. A high voltage is then applied to piezoelectric device 23 of piezoelectric piston device 24 to expand piston device 24 and raise the pressure in wheel cylinder 12. The braking force on the wheel now stops the spinning so that smooth acceleration with minimum slippage between the wheels and the ground is possible.
In the above embodiment fluid pressure was transmitted to the braking device from the master cylinder. There is however the danger that the hydraulic circuit will be damaged or that the transmission of pressure from the master cylinder to the wheel cylinder will be delayed and the responsiveness and reliability of the braking system degraded. With the braking control apparatus described above it is possible to eliminate the hydraulic system for delivering brake fluid pressure from the master cylinder.
FIG. 3 shows another example of a braking system using control apparatus 10. Braking control apparatuses 10 are provided for each wheel 30-33. Brake fluid is supplied from reserve tank 40 to control valve 28 of each apparatus. Each apparatus is controlled by commands from control unit 29. Detection signals are supplied brake operation detector 41 to control unit 29.
Brake operation detector 41 is constructed of piezoelectric elements which produce a voltage signal when brake pedal 36 is operated. This signal is supplied to control unit 29. It is possible that a potentiometer be used to detect the stroke of brake pedal 36.
When control unit 29 receives such a detection signal, the voltage to piezoelectric device 23 is switched to low level which then contracts and the pertinent control valve 28 closes passage 27. In this state, the pressure in hydraulic chamber 20 of wheel cylinder 12 increases with the expansion of piezoelectric piston device 24 and by controlling the voltage to piezoelectric device 23 it is possible to vary the braking force. The voltage supplied to piezoelectric device 23 is controlled based on the detection signal from brake operation detector 41 so that the braking force on the wheels corresponds to the force applied to brake pedal 36.
The voltage supplied to piezoelectric device 23 may be controlled by an analog value corresponding to the force applied to brake pedal 36, however, it is also possible to form a pulse signal whose duty cycle is set corresponding to the detection signal from detector 41 by control unit 29. This pulse signal is then sent to piezoelectric device 23. As the expansion of piezoelectric piston 24 is controlled by the duty cycle of the pulse signal supplied from control unit 29, it is possible to digitalize the control of the braking force. In this case, the pressure of the brake pad against the brake disc is detected by piezoelectric elements, for example, and the detection signal is supplied to control unit 29 to provide a feedback control in which the braking is controlled in response to the detection signal. This provides a reliable braking force which corresponds to the force applied to brake pedal 36 and is uniform for all wheels.
The antiskid control and traction control are both performed by contracting piezoelectric piston device 24 when the fluid pressure in wheel cylinder 12 is high.
With this kind of braking control system in which operation of brake pedal 36 is electrically detected and braking commands are issued from control unit 29, backup structure can be provided in case any part of the command means is damaged.
FIG. 4 shows an example of such back-up structure which includes an emergency power source 42. This power source is employed when, for example, it is detected that power has been cut off to control unit 29 so that braking is automatically performed. When the voltage generated by emergency power source 41 is controlled directly by the detection signal from the braking operation detector 41, it is possible to provide a braking force corresponding to the force applied to brake pedal 36.
If manual control apparatus 43 is provided to vary the voltage generated from power source 42, it becomes possible to control the braking force using manual control apparatus 43.
FIG. 5 shows another example of a control system. Control valves 46 and 47 are provided in the pipes 44 and 45 between reserve tank 40 and the front wheels 30, 31 and the rear wheels 32, 33. Control valves 46 and 47 normally are open and, when a malfunction occurs in all or part of the front or rear wheel system, valve 46 or 47 closes to shut off the system in which the malfunction has occurred.
Volume control devices 48 and 49 are provided in pipes 46 and 47 for emergency use. These devices each comprise a PS pump and an accumulator, etc. and have the function of supplying brake fluid to pipes 46 and 47. When a malfunction is detected in control unit 29, a command is sent to both control valves 46 and 47 or to only the one for the system in which a malfunction has occurred, and the corresponding pipe is closed off. This state is the same as when control valve 28 of braking control apparatus 10 is closed so it is possible to generate a braking force using the pressure generated by emergency volume control device 48 or 49.
FIG. 6 shows another example of braking control apparatus 10 in which wheel cylinder 12 is formed in brake caliper 11. Brake piston 51, which is provided in wheel cylinder 11, has brake pad 12 attached to it. Brake fluid from the master cylinder is supplied to wheel cylinder 12 via port 50. Fluid pressure in wheel cylinder 12 goes up when the brake pedal is operated and drives brake piston 51.
Guide cylinder 52 is also formed inside brake caliper 11 coaxial with wheel cylinder 12. Guide cylinder 52 and wheel cylinder 12 are partitioned by wall 53. Housing 54 is provided inside guide cylinder 52 movable along the axis of cylinder 52. Housing 54 has a cylindrical shape that fits the inside surface of guide cylinder 52 and the portion facing wall 53 is sealed by a bottom plate. Control cylinder 55 is formed coaxially inside guide cylinder 52.
Piezoelectric piston device 56, which is constructed of piezoelectric elements laminated on a plurality of plates, is provided inside control cylinder 55. One surface of this laminated structure abuts against the bottom plate of housing 54. The opening of control cylinder 55 is sealed by lid plate 57 and hydraulic chamber 58 is formed between plate 57 and piezoelectric piston device 56. Spring 59 is provided between plate 57 and piezoelectric piston device 56 and urges the piezoelectric elements that comprise piston device 56 toward the bottom plate of housing 54.
A plurality of cylinder holes, into which are inserted small pistons 601, 602, . . . , are formed parallel to the axis of guide cylinder 52 in lid plate 57, which forms hydraulic chamber 58. Small pistons 601, 602, . . . , which are attached to displacement member 62, are pushed to the outside of lid plate 57 and are pulled into hydraulic chamber 58 by the changes in pressure in hydraulic chamber 58. Displacement member 62 is driven parallel to the axis of guide cylinder 52 in response to the pressure in hydraulic chamber 58.
The surface area of the working surface facing hydraulic chamber 58 is larger than the area of the working surface of small pistons 601, 602, . . . so displacement member 62 is displaced by a greater amount than is piezoelectric piston device 56. Shaft 63 is integrally attached to displacement member 62. Shaft 63 passes through plate 57, the central axis portion of piezoelectric piston device 56, the bottom plate of guide cylinder 52 and wall 53, and is coupled to brake piston 51, so that displacement member 62 together with brake piston 51 moves inside wheel cylinder 51.
Housing 54 moves inside guide cylinder 52. When fluid pressure in wheel cylinder 12 rises and brake piston 51 starts to move, housing 54 moves together with it. However, housing 54 may be fastened inside guide cylinder 52, if necessary. In this case, spring 65 pushes housing 54 away from brake disc 16 so brake piston 51 moves away from brake disc 16.
A plurality of openings are formed in housing 54 facing the inner periphery of guide cylinder 52 and at right angles to the axis of cylinder 52. Piezoelectric devices 641, 642, . . . formed of a plurality of laminated thin-plate piezoelectric elements are housed in these openings and are expanded by the application of a high voltage so that they protrude from the openings in housing 54 and abut against the inner peripheral surface of guide cylinder 52. In this state housing 54 is held against the inside of guide cylinder 52.
In normal operation when the fluid pressure in the master cylinder increases as a result of the operation of the brake pedal, the fluid is supplied to wheel cylinder 12, brake piston 51 is driven and a braking force is applied to brake disc 16. During such normal operation a high voltage is not applied to piezoelectric devices 641, 642, . . . so they are contracted and do not contact the inside surface of guide cylinder 52. In other words, housing 54 is able to move freely inside guide cylinder 52 and so moves together with brake piston 51.
In this kind of normal braking control situation, when the brake pedal is depressed hard and high brake fluid pressure is produced locking the wheels, a wheellock signal is generated based on which a high voltage is applied to piezoelectric devices 641, 642, . . . which expand and hold housing 54 against the inside of guide cylinder 52 at the position in which it was located at the time. In this state piston device 56 contracts without a high voltage being applied.
A high voltage is applied to the piezoelectric elements of piston device 56 with housing 54 being held against guide cylinder 52 and piston device 56 expands decreasing the volume of hydraulic chamber 58 inside housing 54 to push small pistons 601, 602, . . . from hydraulic chamber 58. Then displacement member 62 is moved by small pistons 601, 602, . . . and brake piston 51 pulls pad 14 away from brake disc 16. In other words, the braking force acting on brake disc 16 is reduced and the wheels are unlocked.
It is also possible to prevent wheel spin from occurring during acceleration. As the brake pedal is not operated at this time, the brake fluid pressure in wheel cylinder 12 is low and brake piston 51 is in a position where it cannot exert a braking force on disc 16. When the wheels spin in this state, piezoelectric piston device 56 of the spinning wheel is expanded. Then a high voltage is applied to piezoelectric devices 641, 642, . . . to hold housing 54 in a position facing wheel cylinder 12.
If a high voltage is then applied to piston device 56 to expand it, brake piston 51 will move toward brake disc 16 and the spinning will be stopped, resulting in the smooth acceleration of the automobile.
FIG. 7 shows a variation on the above embodiment. In the embodiment of FIG. 6, shaft 63 was integrally coupled with displacement member 62 and not with piezoelectric piston device 56. However, in this embodiment shaft 63 passes through the center of displacement member 62 in the axial direction so that they can move together. When a high voltage is applied to displacement member 62, shaft 63 is gripped as a result of piezoelectric devices 701, 702, . . . . Piezoelectric devices 711, 712, . . . are provided to force the displacement member 62 against the inner surface of guide cylinder 52 when a high voltage is applied. Displacement member 62 can therefore be selectively held in any position inside guide cylinder 52.
Housing 52, which houses piezoelectric piston device 56, is provided with piezoelectric devices 721, 722, . . . for gripping shaft 63 when a high voltage is applied so that housing 52 can be selectively coupled with shaft 63. The rest of the structure is the same as in FIG. 6 so the same reference numerals have been applied and a description is omitted.
In this embodiment, shaft 63 and displacement member 62 are coupled by applying a high voltage to piezoelectric devices 701, 702, . . . , which is the same as the embodiment of FIG. 6. In this case a high voltage is not applied to piezoelectric devices 721, 722, . . . . Separate operations are possible by releasing the coupling between displacement member 62 and shaft 63 and applying a high voltage to piezoelectric devices 721, 722, . . . , housing 54 and shaft 63 are coupled, or by applying a high voltage to piezoelectric devices 711, 712, . . . and coupling the inner surface of guide cylinder 52 and displacement member 62. Movement is controlled by piezoelectric piston device 56 with housing 54 at the displacement member 62 position being the standard position. When piezoelectric piston device 54 is expanded with housing 54 in this position, piston 51 driven to generate a braking force.
By coupling either shaft 63 and displacement member 62 or housing 54 and displacement member 62, the direction of the braking force corresponding to the expansion of piezoelectric piston device 56 is reversed, making it possible to select either an antiskid force or a traction control force with an extremely simplified control system.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US3313381 *||Jul 2, 1964||Apr 11, 1967||Borg Warner||Electro-magnetic braking system|
|US4130188 *||Aug 1, 1977||Dec 19, 1978||Askew Crawford S||Braking device for a motor|
|US4228874 *||Oct 18, 1978||Oct 21, 1980||K. Ernst Brinkmann, Industrieverwaltung||Electromagnetic brake|
|US4299312 *||Oct 16, 1979||Nov 10, 1981||Sab Industri A.B.||Electromagnetic track brake for a railway vehicle|
|US4433757 *||Mar 1, 1982||Feb 28, 1984||General Motors Corporation||Disc brake lining retainer and wear warning arrangement|
|US4435021 *||Sep 15, 1980||Mar 6, 1984||Lucas Industries Limited||Vehicle brake actuator and braking system|
|US4553059 *||Sep 26, 1984||Nov 12, 1985||Nippon Soken, Inc.||Piezoelectric actuator and a piezoelectric pump injector incorporating the same|
|US4570095 *||Oct 10, 1984||Feb 11, 1986||Nec Corporation||Mechanical amplification mechanism combined with piezoelectric elements|
|US4570098 *||Jun 18, 1984||Feb 11, 1986||Nippon Soken, Inc.||Temperature compensated stack of piezoelectric elements|
|JPS59199352A *||Title not available|
|1||*||Four Years of Experience with 4 Wheel Antiskid Brake Systems (ABS), Heinz Leiber et al, pp. 1 8.|
|2||Four Years of Experience with 4-Wheel Antiskid Brake Systems (ABS), Heinz Leiber et al, pp. 1-8.|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US4690465 *||May 21, 1986||Sep 1, 1987||Nippon Soken, Inc.||Antiskid hydraulic pressure modulator for vehicle hydraulic braking system|
|US4705323 *||Jun 12, 1986||Nov 10, 1987||Nippondenso Co., Ltd.||Brake control apparatus for vehicle|
|US4709969 *||Jul 23, 1986||Dec 1, 1987||Robert Bosch Gmbh||Brake pressure booster in vehicle brake systems|
|US4726549 *||Aug 21, 1986||Feb 23, 1988||Fag Kugelfischer Georg Schafer (Kgaa)||Electromagnetically actuatable pressure modulator|
|US4729459 *||Sep 30, 1985||Mar 8, 1988||Nippon Soken, Inc.||Adjustable damping force type shock absorber|
|US4738493 *||May 19, 1986||Apr 19, 1988||Nippon Soken, Inc.||Automobile antiskid hydraulic braking system|
|US4743791 *||Oct 31, 1986||May 10, 1988||Canon Kabushiki Kaisha||Vibration wave motor|
|US4765140 *||Jan 3, 1986||Aug 23, 1988||Nippondenso Co., Ltd.||Piezoelectric servomechanism apparatus|
|US4848852 *||Nov 12, 1986||Jul 18, 1989||Toyota Jidosha Kabushiki Kaisha||Braking system for automotive vehicle|
|US4854424 *||Apr 18, 1988||Aug 8, 1989||Honda Giken Kogyo Kabushiki Kaisha||Piezoelectric brake device|
|US4860859 *||Apr 18, 1988||Aug 29, 1989||Honda Giken Kogyo Kabushiki Kaisha||Brake device|
|US4890027 *||Nov 21, 1988||Dec 26, 1989||Hughes Aircraft Company||Dynamic motor controller|
|US4894555 *||Nov 19, 1987||Jan 16, 1990||Akebono Brake Industry Co., Ltd.||Brake control system and method for a vehicle|
|US4934761 *||Feb 23, 1989||Jun 19, 1990||Regie Nationale Des Usines Renault||Pressure-generating device for braking circuits of motor vehicles|
|US4995587 *||Nov 3, 1989||Feb 26, 1991||Martin Marietta Corporation||Motion amplifier employing a dual piston arrangement|
|US5046404 *||Nov 19, 1990||Sep 10, 1991||Schnorenberg Jr Walter H||Magnetic disk brake retractor|
|US5067778 *||Nov 19, 1990||Nov 26, 1991||Testardi David A||High performance anti-lock brake system for original equipment and after-market applications|
|US5090518 *||May 31, 1990||Feb 25, 1992||General Motors Corporation||Brake control system|
|US5150772 *||Dec 19, 1990||Sep 29, 1992||General Motors France||Disc brake caliper with an integral proportioning valve|
|US5182484 *||Jun 10, 1991||Jan 26, 1993||Rockwell International Corporation||Releasing linear actuator|
|US5209154 *||Feb 10, 1992||May 11, 1993||Allied-Signal Inc.||Dual area brake actuation piston mechanism|
|US5378120 *||Feb 22, 1994||Jan 3, 1995||Alliedsignal Inc.||Ultrasonic hydraulic booster pump and braking system|
|US5469138 *||May 28, 1993||Nov 21, 1995||Tsai; Hsin-Tan||Danger detector-type automatic control device|
|US5645143 *||Mar 26, 1996||Jul 8, 1997||Lucas Industries Public Limited Company||Electronically controllable braking system for ground vehicles and method for operating same|
|US5826683 *||Jan 28, 1997||Oct 27, 1998||Akebono Brake Industry Co., Ltd.||Magnetostrictive brake|
|US5941611 *||Jan 21, 1997||Aug 24, 1999||Hydraulik-Ring Antriebs- Und Steuerungstechnik Gmbh||Actuating device for brakes of a vehicle, preferably a motor vehicle|
|US6170921 *||Jan 21, 1999||Jan 9, 2001||Meritor Heavy Vehicle Systems, Llc||Magnetostrictive brake actuation mechanism|
|US6176352 *||Oct 2, 1997||Jan 23, 2001||Continental Aktiengesellschaft||Electric brake system for a motor vehicle|
|US6213564 *||Mar 19, 1999||Apr 10, 2001||Face International Corp||Anti-lock brake system with piezoelectric brake actuator|
|US6293632||Jun 11, 1999||Sep 25, 2001||John F. Grote||Vehicular brake-by-wire system|
|US6450588||Jul 3, 2001||Sep 17, 2002||Control System Technology, Inc.||Vehicular brake-by-wire system|
|US6508522 *||Mar 5, 2002||Jan 21, 2003||Delphi Technologies, Inc.||Model based brake pressure estimation|
|US6552473 *||Jun 29, 2001||Apr 22, 2003||C. R. F. Societa Consortile Per Azioni||Control valve with a self-compensating piezoelectric actuator|
|US6717332||Jan 29, 2001||Apr 6, 2004||Viking Technologies, L.C.||Apparatus having a support structure and actuator|
|US6737788||Feb 20, 2003||May 18, 2004||Viking Technologies, L.C.||Apparatus having a pair of opposing surfaces driven by a piezoelectric actuator|
|US6759790||Mar 27, 2002||Jul 6, 2004||Viking Technologies, L.C.||Apparatus for moving folded-back arms having a pair of opposing surfaces in response to an electrical activation|
|US6870305||May 14, 2004||Mar 22, 2005||Viking Technologies, L.C.||Apparatus for moving a pair of opposing surfaces in response to an electrical activation|
|US6879087||Feb 6, 2002||Apr 12, 2005||Viking Technologies, L.C.||Apparatus for moving a pair of opposing surfaces in response to an electrical activation|
|US6975061||Nov 24, 2004||Dec 13, 2005||Viking Technologies, L.C.||Apparatus for moving a pair of opposing surfaces in response to an electrical activation|
|US7021727 *||Apr 6, 2004||Apr 4, 2006||Advics Co., Ltd.||Vehicle brake system for preventing brake noise|
|US7368856||Apr 5, 2004||May 6, 2008||Parker-Hannifin Corporation||Apparatus and process for optimizing work from a smart material actuator product|
|US7564171||Jun 20, 2005||Jul 21, 2009||Parker-Hannifin Corporation||Apparatus and process for optimizing work from a smart material actuator product|
|US8089736 *||Mar 24, 2009||Jan 3, 2012||Hong Fu Jin Precision Industry (Shenzhen) Co., Ltd.||Driving device and protection method thereof|
|US8499907 *||Sep 24, 2003||Aug 6, 2013||Bell Helicopter Textron Inc.||Piezoelectric liquid inertia vibration eliminator|
|US8720652 *||Aug 3, 2009||May 13, 2014||GM Global Technology Operations LLC||Brake retraction utilizing active material actuation|
|US8882091||Nov 11, 2011||Nov 11, 2014||Textron Innovations Inc.||Vibration isolation system|
|US9297439||Mar 12, 2009||Mar 29, 2016||Textron Innovations Inc.||Method and apparatus for improved vibration isolation|
|US9446841||Dec 18, 2008||Sep 20, 2016||Textron Innovations Inc.||Method and apparatus for improved vibration isolation|
|US20040040797 *||Aug 30, 2002||Mar 4, 2004||Plude Leo W.||Electromechanical aircraft brake system and method incorporating piezoelectric actuator subsystem|
|US20040206589 *||Apr 6, 2004||Oct 21, 2004||Masahiko Kamiya||Vehicle brake system for preventing brake noise|
|US20060108861 *||Nov 22, 2005||May 25, 2006||Mando Corporation||Electronic control brake system with piezoelectric actuator|
|US20060151272 *||Sep 24, 2003||Jul 13, 2006||Smith Michael R||Piezoelectric liquid inertia vibration eliminator|
|US20100109590 *||Mar 24, 2009||May 6, 2010||Hong Fu Jin Precision Industry (Shenzhen)Co., Ltd.||Driving device and protection method thereof|
|US20100193299 *||Aug 3, 2009||Aug 5, 2010||Gm Global Technology Operations, Inc.||Brake retraction utilizing active material actuation|
|CN103016573A *||Dec 20, 2012||Apr 3, 2013||江苏大学||Complete disc anti-blocking brake|
|CN103016573B *||Dec 20, 2012||Jan 27, 2016||江苏大学||一种全盘式防抱死制动器|
|DE4125150A1 *||Jul 30, 1991||Feb 4, 1993||Teves Gmbh Alfred||Force modulator esp. for hydraulic antilock braking system - has diaphragm in fluid chamber deformable for compensation of pressure on foot retracted from slotted piston|
|EP0518262A2 *||Jun 9, 1992||Dec 16, 1992||Rockwell International Corporation||Linear actuator|
|EP0518262A3 *||Jun 9, 1992||Feb 15, 1995||Rockwell International Corp||Title not available|
|U.S. Classification||188/72.1, 303/115.2, 303/113.1, 303/68, 188/106.00P, 188/72.3, 188/158, 188/72.4, 310/328|
|International Classification||F16D65/18, F16D55/224, B60T8/48, B60T8/42, H01L41/09, B60T8/36, F16D65/14|
|Cooperative Classification||B60T8/4809, F16D65/18, F16D2121/28, F16D2121/02, F16D2123/00, F16D2125/10, B60T8/4266, F16D55/224, B60T8/369|
|European Classification||F16D65/18, B60T8/48B, B60T8/36F10, F16D55/224, B60T8/42A6|
|Jan 3, 1986||AS||Assignment|
Owner name: NIPPON SOKEN, INC., IWAYA 14, SHIMOHASUMI-CHO, NIS
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:IMOTO, YUZO;HATTORI, YOSHIYUKI;TAKEI, TOSHIHIRO;AND OTHERS;REEL/FRAME:004500/0386
Effective date: 19851213
Owner name: NIPPONDENSO CO., LTD., 1-1, SHOWA-CHO, KARIYA-SHI,
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:IMOTO, YUZO;HATTORI, YOSHIYUKI;TAKEI, TOSHIHIRO;AND OTHERS;REEL/FRAME:004500/0386
Effective date: 19851213
|Jun 8, 1990||FPAY||Fee payment|
Year of fee payment: 4
|May 31, 1994||FPAY||Fee payment|
Year of fee payment: 8
|Mar 16, 1998||AS||Assignment|
Owner name: THK CO., LTD., JAPAN
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TERAMACHI, HIROSHI;REEL/FRAME:010226/0568
Effective date: 19880328
Owner name: THK CO., LTD., JAPAN
Free format text: ;ASSIGNOR:TERAMACHI, HIROSHI;REEL/FRAME:009046/0367
Effective date: 19880328
|Jun 2, 1998||FPAY||Fee payment|
Year of fee payment: 12